WO2012136496A1 - Pièce d'insertion pour garniture d'étanchéité d'arbre - Google Patents

Pièce d'insertion pour garniture d'étanchéité d'arbre Download PDF

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Publication number
WO2012136496A1
WO2012136496A1 PCT/EP2012/055273 EP2012055273W WO2012136496A1 WO 2012136496 A1 WO2012136496 A1 WO 2012136496A1 EP 2012055273 W EP2012055273 W EP 2012055273W WO 2012136496 A1 WO2012136496 A1 WO 2012136496A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
shaft
diameter
dry gas
labyrinth
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2012/055273
Other languages
German (de)
English (en)
Inventor
Gesinus Mateman
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=45952488&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2012136496(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to EP12713650.5A priority Critical patent/EP2663791B1/fr
Priority to RU2013149860/06A priority patent/RU2589415C2/ru
Priority to CN201280017305.2A priority patent/CN103459903B/zh
Priority to US14/110,198 priority patent/US9518473B2/en
Publication of WO2012136496A1 publication Critical patent/WO2012136496A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/002—Sealings comprising at least two sealings in succession
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
    • F04D29/124—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps with special means for adducting cooling or sealing fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings

Definitions

  • the invention relates to a shaft seal insert for a shaft seal of a turbomachine, which extends in an axial direction along an axis of rotation, comprising
  • a rotor part which is designed such that it is on a shaft of a along the axis of rotation
  • stator part which is designed such that it can be inserted into a stator recess
  • At least one dry gas seal which is a on the
  • Rotor member mounted rotating sealing element and attached to the stator part standing sealing element has for sealing a gap between the rotating sealing element and the stationary sealing element, wherein the standing sealing element and the rotating sealing element at a radially and extending in the circumferential direction
  • Sealing surface are arranged opposite to each other, wherein the shaft seal insert at one axial end a
  • Dry gas seals are called shaft seals in
  • Turbomachinery for example in turbocompressors
  • Present invention are shaft seals which have at least two extending around the shaft in the circumferential direction (relative to the axis of rotation) sealing elements, each at least one to the opposite
  • At least one of the mutually facing sealing surfaces has projections and / or recesses, which provide in cooperation with a sealing gas for the construction of a gas film between the two sealing elements on the sealing surfaces, so that the dry gas seal during the intended rotation
  • the dry gas seal requires a clean seal gas, which has substantially no liquid components to seal damage-free or contactless.
  • Projections may have different shapes and are preferably provided on only one sealing surface, preferably on the sealing surface of the rotating sealing element.
  • Recesses may be U-shaped or Tannenbaum-like or T-shaped or in the manner of a spiral, so that there is a formation of a stable sealing film of the sealing gas between the two sealing surfaces.
  • Lubricating oil is needed, such as in seals that work with liquids or compared to a labyrinth seal. Dry gas seals are regularly applied to a high-pressure side with a sealing gas, with a slight leakage of this gas seal the
  • Dry gas seal from the high pressure side to a side of lower pressure - a low pressure side - happens where usually a discharge of this leakage takes place in a so-called vent line. Also, to reduce the consumption of the specially prepared gas seal, is the
  • Dry gas seal regularly surrounded by other shaft seal, especially on the high pressure side is regularly a labyrinth seal, which reduces the outflow of the sealing gas to the side facing away from the dry gas seal side high pressure side.
  • the main reason for the serial additional seal, in particular labyrinth seal is the sealing effect on failure of the dry gas seal.
  • dry gas seals that use a gas seal as have central supply line of the sealing surfaces are usually protected by means of a serial additional seal, in particular labyrinth seal against contamination.
  • On the high pressure side of the dry gas seal is usually a process gas, which is in the case of a turbocompressor under an operating pressure. The sealing gas must have an overpressure relative to this process gas in order to achieve this
  • the invention has set itself the task of reducing the complexity of a turbomachine having a shaft seal insert of the type described above, to simplify the assembly of such a turbomachine and the
  • the axis of rotation is a central axis of the shaft seal insert used as
  • Rotation axis is called, since it is in the
  • Shaft seal acts naturally surrounding a rotating shaft in an operation.
  • the terms high-pressure side and low-pressure side are used, which indicates that the shaft seal against a
  • Pressure difference prevents overflow of a fluid from one side of higher pressure to a side of lower pressure and, accordingly, maintains the pressure difference.
  • stator part is to be understood as a stationary component, which is carrier of components at least the dry gas seal of the shaft seal insert.
  • the stator part is designed such that it can be inserted into a recess of a stator, which stator is preferably designed as a housing of the turbomachine. This may also be connected to the housing components, so that an indirect connection of the stator is provided with a housing of a turbomachine.
  • the stator is suitable to the components of
  • the shaft seal insert in a unit summarized, so that it is the shaft seal insert is a movable module that can be attached as part of the assembly as a whole on the shaft of a rotor.
  • the shaft seal insert according to the invention is first attached to the shaft and then inserted together with the shaft in, for example, a pot housing or inserted into a lower housing half and fixed in the housing.
  • Labyrinth seal part as parts of the stator or the rotor part is to be understood such that even an at least partially integral formation of these two
  • Attachment of the labyrinth seal parts to the sleeves is to be understood as a releasable attachment, which in particular alternatively to the at least partially integral
  • vibration amplitudes turn out lower and increase any resonant frequencies due to the stiffening advantageous.
  • this allows a reduction in the shaft diameter, so that assuming the same radial play demand a smaller area is sealed by the shaft seal, so that only a smaller potential leakage amount is created and increases the efficiency of the turbomachine.
  • Shaft seal insert can get.
  • the shaft seal insert on the stator part is expediently provided with a second stationary seal, so that the stator part
  • stator can be used sealingly in a recess of the stator.
  • the rotor part is advantageously provided with a stationary seal, so that the rotor part is sealingly attachable to the shaft of a rotor.
  • the shaft of the rotor can be provided with a shoulder on which the
  • Rotor part comes with a contact surface for axial abutments.
  • seals may also be used, for example elastomeric O-ring seals.
  • the invention is not limited to one
  • Diameter is arranged coaxially to the axis of rotation, wherein the outermost diameter of the sealing surfaces of
  • Dry gas seal is smaller than the fifth diameter.
  • Dry gas seal one for the thrust bearing still bearable change of the thrust on the rotor causes.
  • Diameter coaxial with the axis of rotation is substantially identical to a fourth diameter, on which there is a fourth stationary seal between the stator and the stationary sealing element of the dry gas seal.
  • the difference between the fourth diameter and the fifth diameter is less than 10% of the fifth diameter.
  • the sealing gas is useful for a process gas on the other side of the
  • Dry gas seal is expediently provided a seal derivation, which feeds the pure gas seal gas possibly as a mixture with a pending on the low pressure side of other gas seal gas treatment or one
  • Embodiment of the invention result. Show it:
  • Figure 2 is a longitudinal section through a
  • Circumferential direction, diameter and radius relate to a rotation axis AX, which is a central axis of a shaft seal insert DGSM according to the invention.
  • the shaft seal insert DGSM shown in FIGS. 1 and 2 comprises a stator part CS and a rotor part RS as well as a dry gas seal DGS and a labyrinth seal LS.
  • the rotor part RS of the shaft seal insert DGSM is sealingly mounted on a shaft SH of a rotor R by means of a second static seal STS2.
  • the wave is SH
  • Turbomachine CO which is formed in a manner not shown as a centrifugal compressor.
  • the stator part CS is by means of a first stationary
  • the first stationary seal STS1 and the second stationary seal STS2 have a V-profile which extends in a respective circumferentially extending one
  • the shaft seal insert DGSM has a high-pressure side HPS and a low-pressure side LPS, the high-pressure side HPS being exposed to a process gas which is under overpressure in relation to the low-pressure side LPS.
  • the stator part is additionally sealed with respect to the stator recess CR with a static seal STS11.
  • Shaft seal insert DGSM is shown in FIGS. 1, 2
  • Rotor part RS is by means of the dry gas seal DGS
  • Dry gas seal DGS serves to reduce the
  • Process gas PG has an overpressure.
  • Low pressure side LPS of the dry gas seal DGS is a seal leakage SGE of only small leakage of
  • Dry gas seal DGS provided, which opens into a vent or flaring preferred.
  • the dry gas seal DGS has a rotating sealing element RSE and a stationary sealing element SSE, which are connected to a respective sealing surface on a common sealing surface
  • the rotating sealing element RSE is opposite to the rotor part RS by means of a third stationary seal SS3, which is located on a third diameter DSS3 extends in the circumferential direction, sealed from the differential pressure.
  • the stator part CS has an elastic element EE, which biases the standing sealing element SSE against the rotating sealing element RSE by means of a piston PT.
  • the standing sealing element SSE is opposite to the guide ring GD by means of a fourth
  • the labyrinth seal LS has a standing
  • Labyrinth seal part RLSM which extends in an axially and circumferentially extending central
  • Labyrinth seal surface LSS face each other, wherein the labyrinth seal surface LSS extends in the circumferential direction on a fifth diameter DSS5.
  • the mean labyrinth seal surface is to be understood as meaning an area which extends axially and circumferentially along the fifth diameter DSS5, the fifth diameter resulting from a
  • Diameter the low pressure side inner diameter of the opening of the labyrinth seal LS.
  • the rotating sealing element RSE stands upright
  • Sealing element SSE has a specially formed surface on a standing sealing surface DGSTS, which faces the dry gas seal sealing surface DGSS. Training the surface is the opposite rotating
  • Sealing surface DGSRS adapted such that a non-contact operation of the dry gas seal DGS to form a corresponding lubricating film of the sealing gas SG
  • Labyrinth seal LS and components of the dry gas seal DGS is possible.
  • the labyrinth seal LS overlaps axially with the rotating one
  • FIG. 2 shows a design which is suitable in particular for high-pressure application at differential pressures of more than 200 bar.
  • the labyrinth sealing surface LSS is located on a substantially identical diameter as the fourth stationary seal SS4 between the rotor part RS and the rotating sealing element RSE.
  • the difference between the fifth diameter DSS5 and the fourth diameter DSS4 is less than 10% of the fifth diameter DSS5.
  • Diameter DSS4 less than 10% of the fourth diameter DSS5.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pièce d'insertion de garniture d'étanchéité d'arbre (DGSM) conçue pour une garniture d'étanchéité d'arbre (SHS) d'une turbomachine (CO), qui s'étend dans une direction axiale le long d'un axe de rotation (AX), comprenant : une partie rotor (RS) conçue de manière à pouvoir être disposée sur un arbre (SH) d'un rotor (R) s'étendant le long de l'axe de rotation (AX), une partie stator (CS) conçue de manière à pouvoir être insérée dans un évidement de stator (CR), comprenant au moins une garniture d'étanchéité à gaz sec (DGS) qui comporte un élément étanche rotatif (RSE) disposé sur la partie rotor (RS) et un élément étanche fixe (SSE) disposé sur la partie stator (CS) pour étanchéifier un espace intermédiaire (IR) entre l'élément étanche rotatif (RSE) et l'élément étanche fixe (SSE), l'élément étanche fixe (SSE) et l'élément étanche rotatif (RSE) étant disposés l'un en face de l'autre sur une surface étanche s'étendant de manière radiale et en direction périphérique, ladite pièce d'insertion de garniture d'étanchéité d'arbre (DGSM) comportant un côté haute pression (HPS) au niveau d'une extrémité axiale et un côté basse pression (LPS) au niveau de l'autre extrémité axiale. L'objectif de cette invention est de pouvoir produire une turbomachine particulièrement compacte. A cet effet, une garniture d'étanchéité à labyrinthe (LS) est prévue côté haute pression (HPS) pour étanchéifier l'espace intermédiaire (IR) dans un agencement en série par rapport à la garniture d'étanchéité à gaz sec (DGS), cette garniture d'étanchéité à labyrinthe comprenant une partie de garniture d'étanchéité à labyrinthe fixe (SLSM) et une partie de garniture d'étanchéité à labyrinthe rotative (RLSM), la partie de garniture d'étanchéité à labyrinthe fixe (SLSM) formant une partie de la partie stator (CS) ou étant disposée de manière fixe sur celle-ci, et la partie de garniture d'étanchéité à labyrinthe rotative (RLSM) formant une partie de la partie rotor (RS) ou étant disposée de manière fixe sur celle-ci.
PCT/EP2012/055273 2011-04-08 2012-03-26 Pièce d'insertion pour garniture d'étanchéité d'arbre Ceased WO2012136496A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP12713650.5A EP2663791B1 (fr) 2011-04-08 2012-03-26 Pièce d'insertion pour garniture d'étanchéité d'arbre
RU2013149860/06A RU2589415C2 (ru) 2011-04-08 2012-03-26 Вставка уплотнения вала
CN201280017305.2A CN103459903B (zh) 2011-04-08 2012-03-26 轴密封插件
US14/110,198 US9518473B2 (en) 2011-04-08 2012-03-26 Shaft seal insert

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011007071A DE102011007071A1 (de) 2011-04-08 2011-04-08 Wellendichtungseinsatz
DE102011007071.0 2011-04-08

Publications (1)

Publication Number Publication Date
WO2012136496A1 true WO2012136496A1 (fr) 2012-10-11

Family

ID=45952488

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/055273 Ceased WO2012136496A1 (fr) 2011-04-08 2012-03-26 Pièce d'insertion pour garniture d'étanchéité d'arbre

Country Status (6)

Country Link
US (1) US9518473B2 (fr)
EP (1) EP2663791B1 (fr)
CN (1) CN103459903B (fr)
DE (1) DE102011007071A1 (fr)
RU (1) RU2589415C2 (fr)
WO (1) WO2012136496A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3000167A1 (fr) * 2012-12-20 2014-06-27 Cryostar Sas Ensemble joint d'etancheite a gaz pour pompes a liquide cryogenique
EP2918846A1 (fr) 2014-03-14 2015-09-16 Siemens Aktiengesellschaft Agencement de joint d'arbre
DE102017223791A1 (de) 2017-12-27 2019-06-27 Siemens Aktiengesellschaft Wellendichtungsanordnung einer Turbomaschine, Turbomaschine

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012223830A1 (de) * 2012-12-19 2014-06-26 Siemens Aktiengesellschaft Abdichtung eines Verdichterrotors
DE102013227208A1 (de) * 2013-12-30 2015-07-02 Siemens Aktiengesellschaft Dichtsystem für eine Dampfturbine sowie Dampfturbine
FI127009B (fi) * 2014-03-27 2017-09-15 Andritz Oy Lipeäsuodin ja menetelmä lipeäsuotimen yhteydessä
DE102014011042A1 (de) * 2014-07-26 2016-01-28 Man Diesel & Turbo Se Strömungsmaschine
CN106014509A (zh) * 2016-07-28 2016-10-12 中国核动力研究设计院 一种以超临界二氧化碳为工质的透平发电机组
EP3293426A1 (fr) * 2016-09-13 2018-03-14 Siemens Aktiengesellschaft Joint etanche aux gaz
EP3293425A1 (fr) * 2016-09-13 2018-03-14 Siemens Aktiengesellschaft Joint etanche aux gaz
IT201700029982A1 (it) * 2017-03-17 2018-09-17 Nuovo Pignone Tecnologie Srl Tenuta a gas
DE102017109663A1 (de) * 2017-05-05 2018-11-08 Man Diesel & Turbo Se Dichtungssystem, Strömungsmaschine mit einem Dichtungssystem und Verfahren zum Reinigen desselben
DE102018202681B3 (de) * 2018-02-22 2019-07-04 Eagleburgmann Germany Gmbh & Co. Kg Gleitringdichtungsanordnung mit geteilter Wellenhülse
EP3862598B1 (fr) * 2020-02-07 2023-05-24 Dresser-Rand SAS Dispositif d'étanchéité d'arbre
US11692628B2 (en) * 2020-10-26 2023-07-04 Changshu Institute Of Technology Sealing device for gas-liquid two-phase fluid medium under variable working conditions
US11572952B2 (en) 2021-05-29 2023-02-07 Dresser-Rand SAS Shaft sealing arrangement

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DE4225642C1 (fr) * 1992-07-02 1993-07-29 Sulzer-Escher Wyss Ag, Zuerich, Ch
EP0781948A1 (fr) * 1995-12-29 1997-07-02 Sulzer Turbo AG Turbomachine pour gaz non-parfait
DE102009012038A1 (de) * 2009-03-10 2010-09-16 Siemens Aktiengesellschaft Wellendichtung für eine Strömungsmaschine

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CA2041469A1 (fr) 1991-04-30 1992-10-31 Clayton Bear Ensemble de joints d'etancheite disposes dans un meme plan
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JP2004308754A (ja) 2003-04-04 2004-11-04 Mitsubishi Heavy Ind Ltd 軸封装置
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Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
DE4225642C1 (fr) * 1992-07-02 1993-07-29 Sulzer-Escher Wyss Ag, Zuerich, Ch
EP0781948A1 (fr) * 1995-12-29 1997-07-02 Sulzer Turbo AG Turbomachine pour gaz non-parfait
DE102009012038A1 (de) * 2009-03-10 2010-09-16 Siemens Aktiengesellschaft Wellendichtung für eine Strömungsmaschine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3000167A1 (fr) * 2012-12-20 2014-06-27 Cryostar Sas Ensemble joint d'etancheite a gaz pour pompes a liquide cryogenique
US9476314B2 (en) 2012-12-20 2016-10-25 Cryostar Sas Gas seal assembly for cryogenic liquid turbomachines
EP2918846A1 (fr) 2014-03-14 2015-09-16 Siemens Aktiengesellschaft Agencement de joint d'arbre
DE102017223791A1 (de) 2017-12-27 2019-06-27 Siemens Aktiengesellschaft Wellendichtungsanordnung einer Turbomaschine, Turbomaschine

Also Published As

Publication number Publication date
CN103459903B (zh) 2015-12-23
DE102011007071A1 (de) 2012-10-11
US20140030063A1 (en) 2014-01-30
RU2589415C2 (ru) 2016-07-10
CN103459903A (zh) 2013-12-18
EP2663791B1 (fr) 2015-08-26
RU2013149860A (ru) 2015-05-20
EP2663791A1 (fr) 2013-11-20
US9518473B2 (en) 2016-12-13

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